Crankset based bicycle power measurement

ABSTRACT

The present application relates to an input torque measuring device for a drive train of a bicycle. The drive train includes a first crank arm and a second crank arm. An inboard end of each crank arm is rotatably mounted to the bicycle at a bottom bracket of the bicycle. At least one chain ring is configured to rotate a driven wheel of the bicycle. A spider is connected to the first crank arm adjacent the bottom bracket and extends out to the at least one chain ring. The spider is configured to transmit force applied to the crank arms directly to the at least one chain ring. The spider may include a plurality of sensors configured to respond to the force applied by the spider to the at least one chain ring. The sensors produce an electronic signal relative to the force transmitted by the spider to the at least one chain ring and a processor configured to receive the electronic signals from each sensor of the spider.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application claims priority to U.S. Provisional ApplicationSer. No. 60/864,431, filed on Nov. 6, 2006, the disclosure of which isincorporated herein reference.

BACKGROUND

In the field of bicycle training and racing, a number of objective andsubjective criteria may be used to judge to level and quality of acyclist's performance in a particular event or training activity. Thesecriteria may be used to determine or estimate the cyclist's overallability or training level as well as the cyclist's ability with regardto specific aspects or types of exertion. These criteria may also beused to determine the degree to which that overall ability or specificaspects of ability were utilized in the event or training session. Thisinformation can then be used to tailor specific approaches to futureevents or training activities.

Since some of the criteria that may be used are subjective and mayfluctuate based on a variety of factors that may or may not be apparent,it has become increasingly desirable, among cyclists, to focus on one ormore objective performance measurements. One of these objectivestandards used may be the mechanical power generated by the cyclist thatenables the bicycle to move forward. The speed at which the bicyclemoves is dependent on a wide array of environmental factors andequipment characteristics. Thus, measuring the response to the powergenerated by the cyclist may not be representative of physical workload,as all of the external factors should be accounted for in some fashion.

By measuring the power generated directly, rather than the reaction tothe power generated, a more objective measure of the level of effortexerted by the cyclist may be determined fairly quickly and easily.

Conventional power meters measure power in three primary ways: at thecrankset, in the chain being moved by the crankset, or at the hub beingdriven by the chain. Measurements relying on the chain have beenconventionally indirect and have generally been the least precise andaccurate. Measurement at the driven hub can be quite accurate but thepower measured represents the power generated by the cyclist minus anydrive line losses that occur in the transmission of the power to thehub. In some cases, these losses may be significant and are dependent ona number of external factors, such as the length and quality of thechain, bearing losses, flexibility of the bicycle or components of thedrive line, and other variables. These variables may change over time orbased on the power being generated and transmitted. Thus, measuringpower at the driven hub must also deal with external factors that may beunknown or too variable to accurately account for.

Conventional crankset power measurement systems but may include someinherent inaccuracies or operational issues that will be describedbelow. Improvements to bicycle power measuring systems are desirable.

SUMMARY

The present application relates to an input torque measuring device fora drive train of a bicycle. The drive train includes a first crank armand a second crank arm, each crank arm adapted to be engaged by a riderof the bicycle at an outboard end. An inboard end of each crank arm isrotatably mounted to the bicycle at a bottom bracket of the bicycle. Atleast one chain ring is configured to rotate a driven wheel of thebicycle. The measuring device may include a spider connected to thefirst crank arm adjacent the bottom bracket and extending out to anddirectly supporting the at least one chain ring. The spider isconfigured to transmit force applied to the crank arms directly to theat least one chain ring. The spider may include a plurality of sensorsconfigured to respond to the force applied by the spider to the at leastone chain ring. The sensors produce an electronic signal relative to theforce transmitted by the spider to the at least one chain ring. Thedevice further includes a processor configured to receive the electronicsignals from each sensor of the spider.

The present application further relates to an input torque measuringdevice as described above with the spider including a plurality ofspider arms extending out to and supporting the chain ring.

The present application further relates to an input torque measuringdevice for a drive train of a bicycle. The drive train includes a firstcrank arm and a second crank arm configured to be engaged by a rider ofthe bicycle at an outboard end. An inboard end of each crank arm isrotatably mounted to the bicycle at a bottom bracket of the bicycle. Atleast one chain ring is mechanically connected to the crank arms andconfigured to rotate a driven wheel of the bicycle. The measuring devicemay include at least one of the crank arms with at least one strainmeasurement device configured to generate an electronic signal when aforce is applied to the crank arm. Circuitry may be configured toreceive the electronic signal from the strain measurement device andincluding a processor configured to calculate the magnitude of the forceapplied to the crank arm from the signal generated by the strainmeasurement device.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawing figures, which are incorporated in andconstitute a part of the description, illustrate several aspects of theinvention and together with the description, serve to explain theprinciples of the invention. A brief description of the figures is asfollows:

FIG. 1 is a perspective view of a bicycle crankset spider according tothe present disclosure.

FIG. 2 is a spider and chainrings assembly according to the presentdisclosure including the spider of FIG. 1 and illustrated arrangement ofloads applied to the inner chainring.

FIG. 3 is a perspective view of a first alternative embodiment of aspider arm of a bicycle crankset including laterally mounted straingages according to the present disclosure.

FIG. 4 is a perspective view of a second alternative embodiment of aspider arm of a bicycle crankset including shear web mounted straingages according to the present disclosure.

FIG. 5 is a perspective view of a crank arm of a bicycle cranksetincluding shear web mounted strain gages according to the presentdisclosure.

FIG. 6 is a second opposite view of the crank arm of FIG. 5.

FIG. 7 is a perspective cross-sectional view of a first alternativeembodiment of a crank arm of a bicycle crankset including internal shearweb mounted strain gages according to the present disclosure.

FIG. 8 is a second opposite perspective view of the crank arm of FIG. 7.

FIG. 9 is a perspective view of a pedal end of an alternative embodimentof a crank arm including shear web mounted strain gages according to thepresent disclosure.

DETAILED DESCRIPTION

Two different approaches to power meters or measuring devicesincorporated into bicycle cranksets are described below. A firstapproach involves a system including gages integrated into the crankset“spider” (the portion of the crankset that connects the crank arm to thechain rings). A second approach involves a system that integrates gagesinto the crank arm.

A bicycle crankset as used in this disclosure refers to an assembly ofopposing crank arms rotatably mounted to a bicycle via bottom bracket. Afirst side of the crankset includes a crank arm adapted to mount a pedalat an outer end and adapted for connection to the bottom bracket at theopposite end. This is typically the left crank arm.

A second side of the crankset includes a crank arm which also is adaptedto mount a pedal at the outer end and adapted for connection to thebottom bracket at an opposite end. The second side of the crankset mayalso include a spider 100, such as shown in FIG. 1, to which a chainring may be mounted or which may have integral teeth for engaging abicycle drive chain. A typical spider may have four or five spider arms,typically evenly spaced, with a chain ring mounted at an end of thespider arms and typically fixed in place by a bolt in each spider arm.The spider may be rigidly connected to the crank arm of the second side.The chain and other drive line components are conventionally mounted tothe right side of a bicycle.

The bottom bracket is typically configured to transmit rotation forceexerted on the first side crank arm to the spider on the second side andto the drive chain. Thus, all force generated by a cyclist using thiscrankset will be applied to at least one of the crank arms and alsotransmitted through the spider to exert force on and move the drivechain.

According to the present disclosure, both approaches may calculateoutput power of a cyclist by measuring the torque load applied to thecranks and the crank angular velocity. Crank angular velocity can beeasily measured with numerous sensors designs, whereas the appliedtorque load is somewhat more challenging. Both approaches describedherein utilize a spring element integrated into the crankset thatdeforms a predictable amount under a given load, and a strain gagearrangement to measure the amount of deformation.

The Spider Approach

While pedaling, a cyclist is exerting a torque load between thechainrings and the crank arm. In the “spider” approach, each arm of thechainring spider may be instrumented with strain gages to measure theamount of deformation that occurs in each spider arm under load. Thereis also loading between the chain and the chainring, which is applied tothe chainring in a local area at the top contact point (assuming atypical rear wheel driven bicycle arrangement, with the crankset mountedin front of the rear hub). Because the chain load is applied locally andthe chainring may not be perfectly rigid, the bending load on each ofthe spider's arms may not be evenly distributed at any given point intime when the cyclist is applying force to the crankset.

Therefore, each of the spider's arms may desirably be instrumented.Because the spider arms are the only parts connecting the chainrings tothe crank arm, the sum of the loading on the spider arms will yield thetotal loading between the crank arm and the chainrings. Note that thereare several methods of summing the loads, including measuring each armindividually and summing in embedded software or summing electricallywith a unique arrangement of the strain gages, as will be describedlater.

Alternatively, fewer than all of the spider arms may be instrumented andsome form of algorithm may be used to calculate or interpolate the forceor load exerted by the non-instrumented spider arms. The power generatedby a cyclist may vary during pedaling and this variance may tend to becyclical in nature about each rotation of the crankset. The nature ofthe peaks and valleys of force generated may be unique for each cyclistand these variations may make it difficult to estimate overall force orpower generated with fewer than all of the spider arms instrumented.However, assumption as to a typical cyclist's cycle of power exerted maybe used or specific parameters for each cyclist may be determined andused in the algorithm. To avoid using such algorithms and the necessaryassumptions or prior analysis to calculate a derived power output, itmay be more desirable though not necessary to provide gages on each ofthe spider arms of the crank.

Strain Gage Arrangement

In the spider approach described generally above, only the loads actingin the plane of the spider arms are preferably measured to calculatepower. The chainline is almost never exactly in this plane, as the chainline varies depending on the gear selection and arrangement ofcomponents making up the drive line. This offsetting of the chainlinemay create a lateral load on the spider arm (in the axial direction ofthe bottom bracket). Additionally, the spider may carry multiplechainrings. The center planes of the chainrings are offset from eachother and will be offset from the center plane of the spider. This maycreate a torque about the long axis of the spider arm.

This arrangement of forces or loads is illustrated in FIG. 2. In FIG. 2,spider 100 in incorporated into a crankset 22 with an inner or smallchain ring 24 and an outer or large chain ring 26. Both chain rings areconnected to spider 100 at an outer end of a spider arm 28. In theillustrated force example, a chain is engaged with small chain ring 24and an applied load is applied to the chain through spider 100. Becausethe chain may not pull perfectly in plane with chain ring 24, theapplied force may be comprised of a lateral load and a normal load.Additionally, because chain ring 24 is offset laterally from spider arm28, the applied load also creates a torque load as shown. Preferably,only the normal load is measured, as this is the mechanical force thatgenerates forward of the bicycle. According to the present disclosure,strain gages should preferably not respond to either of the lateral loadand torsion load.

As a background to the following discussion of strain gage locations,the following review of strain gage wiring and measurement methods isprovided. Strain gages are basically resistors whose electricalresistance changes when mechanically distorted. The change in resistanceis proportional to the change in length of the gage. In order tocompensate for numerous other variables that can affect resistance, itis common to place strain gages in pairs such that under load, one gageis under compression (meaning the gage will be shortened, leading toless electrical resistance) and the other is under tension (meaning thegage will be lengthened, leading to more electrical resistance). Theresistance of each gage in the pair may be measured and a ratio of theresistances of the paired gages can be determined with a suitableelectrical circuitry.

The first arrangement is a tension/compression arrangement where astrain gage 10 is placed on each side of a spider arm 12 of a spider 14,as shown in FIG. 3. The strain gage may be located on a raised ridge 20that concentrates strain under the gage.

This arrangement is fairly straightforward; chain tension in the planeof the spider will bend the arm, causing tension under one gage andcompression under the other. The lateral load may be canceled out ineach gage, because the neutral strain axis in this load case runsthrough the center of each gage, with compression on one half, andtension on the other. Overall the net effect on the gage resistance isgenerally zero. Also, the torsion load about the arm's axis iseffectively cancelled out because it generally affects both gagesequally and the result is generally zero when measuring the ratio ofresistance between the gages. Therefore this opposed arrangement ofstrain gages achieves the desired measurement characteristics.

Symmetry may be desirable in the local area 16 between the placement ofgage 10 in order to create this behavior. Similarly, the shape of arm 12beyond the immediate local area 16 will preferably encourage good stress“flow” into the symmetrical area 16 between the gages 10 in order toenhance the performance of the gages. The performance and viability ofthis design has been verified through the use of finite elementanalysis.

Although conceptually sound, there are drawbacks to this design. Straingages 10 are placed on an external surface that is vulnerable to damageand not readily protectable. Similarly, the location is not conducive torouting lead wires nor does it immediately lend itself to easy gageplacement or construction.

A second strain gage arrangement is a shear web, as illustrated in FIG.4. In this arrangement a shear gage 118 may be used. Shear strain gage118 may utilize two strain gage grids 110 arranged at opposing 45 degreeangles on a single gage substrate. When gage 118 is placed under shearstrain, one grid 110 is compressed and the other grid 110 is stretched.In the shear web arrangement, a pocket 120 may be created on each sideof a spider arm 112 of a spider 110, creating a thin web 122 of materialbetween each gage. A pair of gages 118 may be placed on opposite sidesof web 122 and a second pocket 120 may be formed in spider arm 112opposite the first pocket 120 to contain a second gage 118 opposite thefirst gage 118.

Under chain load in the plane of the spider 112, this web 122 will see ashear strain. A shear strain gage 118 may be placed on both sides of theweb 122. The gages 118 may be wired so that the two grid areas 110 (oneof each gage 118 on opposite sides of web 122) under compression are inseries with each other and the two grid areas 110 under tension are inseries with each other. The resistance of strain gages in series willaverage the strain under each of the gages. Lateral loads on the spiderarm may stretch and compress both left and right strain grids equally,and the effect on the ratio is generally zero. Also, torsion loads aboutthe vertical axis of the arm may be essentially cancelled out, in thiscase, the right front and back left grids will see a tension, when theleft front and right back are compressed, or vise versa. Again, due tothe wiring arrangement, the net effect of this load on the resistanceratios may be essentially zero.

The function and performance of this gage arrangement of FIG. 4 has beenverified both through finite element analysis and construction andtesting of a physical prototype. Again, symmetry may be desirable aboutspider arm 112 to achieve the desired performance. Note that a slot 124may be located at the bottom of the shear web. This slot 124 allows forrouting lead wires from one side of the spider 114 to the other. Theplacement of this slot 124 and the material geometry between it and thestrain gages 118 may be designed specifically to minimize the effect ofthe slot on the strain gage measurement.

The shear web arrangement of FIG. 4 may have several advantages in termsof packaging and construction. The strain gages 118 may be placed in thebottom of pocket 120, so that the pocket may enclose and protect thegage from five sides. Only the top is exposed, which can be covered byepoxy, wax, urethane, plastic, silicone or similar encapsulationmaterial or other suitable mechanical cover, filling in pocket 120 atopthe gage. The pocket 120 may be used create reference geometry which maybe used to facilitate the accurate and repeatable placement of thestrain gages 118 on spider 114. Also the gages 118 may be placed on thefront and back of the spider, which introduces possibilities ofintegrating all the grid areas for all five arms onto one largesubstrate that can be affixed at once. This common substrate may improveoverall production or cost efficiency.

As mentioned above, the total torque about the bottom bracket axisgenerated by the cyclist is equal to the sum of the torques that eacharm carries. Also, in the above strain gage arrangements, the resultantstrain is proportional to the applied torque. Therefore, the sum of thestrains is proportional to the sum of the torques.

Depending on the construction of the electronics, each arm can bemeasured independently, and then the independent measurements can beadded together by software to get the total torque.

Alternatively, the strain gages can be physically wired together suchthat one measurement can be taken that is proportional to the totaltorque. Specifically, all the grid areas on the left side of the spiderarms may be wired in series with each other, and all the grid areas onthe right side of the spider arms may be wired in series with eachother. Then just one measurement may be taken and the ratio of all thelefts to all the rights is proportional to the total torque.

Numerous alternative wiring and measurement arrangements can also beconceived, including, but not limited to, pairing spider arms together,and measuring the front sides of the spider arms separately from backside of the spider arms. These variations on wiring and measurementarrangements may yield equivalent primary results, but each may possesdistinct characteristics related to measurement resolution,repeatability, precision as well as fabrication and additionalproperties.

The Crank Arm Approach

The second approach described herein may include placement of a shearweb strain gage arrangement in the crank arm of the crankset. An exampleof this approach is illustrated in FIGS. 5 and 6.

One of the challenges in executing input torque measurement in a crankarm is to isolate the input torque from the other forces acting on thearm. The input force from the cyclist's leg is applied to the pedal,which is cantilevered off the side of the crank arm. This creates atorque around a longitudinal axis of the crank arm. Unfortunately, theradius at which the load is applied is a function of the pedal design,cleat placement on the shoe and the biomechanics of the rider's pedalstroke. Likewise there are other forces acting laterally andlongitudinally along the arm.

The shear web strain gage arrangement addresses these issues. The shearweb arrangement operates similarly to the spider based system above,however in this case the shear web arrangement measures the strain froma location within the crank arm instead of the spider.

Referring to FIGS. 5 and 6, a crank arm 200 may include a first end 206with an opening 208 for mounted a pedal to the crank arm and a secondopposite end 210 with an opening 212 for mounting crank arm 200 to abottom bracket. A pocket 216 may be is machined into both front and backsides of crank arm 200 to create a thinned web section 202. A straingage measurement grid such as gage 118 described above may be mountedwithin the pockets 216 and attached to the front and back faces of web202. Each strain gage 118 may have two grids 110, oriented atapproximately forty-five degrees to the longitudinal axis of crank arm200, and generally ninety degrees from each other. The cross-sectionalarea between the gages (web 202) and in the surrounding local area ofthe arm is preferably symmetrical in order to create well-behaved linearresponses to applied loads. Likewise the local area should be conduciveto even stress flow into the strain gage section.

The creation of pockets 216 for gage placement is conducive to locationand protection of the gages, but is not required for function. The gagesmay be placed on the external surface of the arm and the section betweenthe gages may be hollow or otherwise modified from a thin web sectionprovided the symmetry requirements are met.

Like the spider approach described above, this crank arm arrangement mayallow the torque about the axis of rotation to be measured. Note that inthis approach, the strain gage arrangement does not measure bending dueto the applied load. Gage 118 instead measures shear. This allows thestrain gages to be placed anywhere along the length of the crank arm.The amount of shear measured by gages 118 will be proportional to theload applied to the crank arm, regardless of where along the length ofthe crank arm the gages are placed.

In FIGS. 5 and 6, one possible configuration of crank arm 200 utilizinga shear web strain gage arrangement is illustrated. The electronics forsensing and recording the reaction of the mounted gages may be placedwithin a channel 204 on the back of the crank arm 200.

An alternative embodiment of a crank arm 300 according to the crank armapproach is shown in FIGS. 7 and 8. Crank arm 300 includes the twostrain gages on the internal surface of a hollow crank arm. Althoughconceptually distinct from the shear web of crank arm 200, the executionis very similar. Two strain gages such as gages 118 are used, eachhaving two strain grids oriented generally ninety degrees from eachother and approximately forty-five degrees from a longitudinal axis ofthe crank arm.

FIGS. 7 and 8 show a possible design of crank arm 300 utilizing a dualinternal shear gage arrangement. The electronics may be placed inside ahollow section 302 of the crank arm to provide good protection from theelements. Strain gages 118 may be placed adjacent to first end 306 wherepedal mounting opening 208 is located. As described above, strain gages118 could located at other locations along the length of crank arm 300.

The wiring and measurement of strain gages 118 mounted to any of thecrank arms described above can be executed in much the same manner asthe spider approach described above. However a few changes can be madethat may greatly improve the accuracy of the measurement. In FIG. 9, acrank arm 400 includes a pair of opposing gages 118, each with two grids110. The labeling the four strain gage grids are as follows: SG (StrainGage)—F or B (front or back) and T or B (top or bottom).

In the case of crank arm 400, the primary load along the arm is torsiondue to the torque placed about the longitudinal axis L of the arm. Thiscreates shear on the front and back of the arm in opposite directions.Table 1 shows an example of average strain under each grid 110 ascalculated by finite element analysis. The strain gage measurementelectronics may measure the ratio of resistances of two strain gagegrids. Ultimately the average shear strain of the two gages must becalculated. There are two primary methods that can be used to achievethis.

A first method is to measure the total strain of the front and reargrids independently with the measurement electronics then add themtogether to get the total. One advantage of this method is that thestrain gage measurement electronics will measure higher strain levels,leading to greater accuracy and precision. However, two separatemeasurements must be made in this method.

A second method is to wire the top grids of the front and rear gages inseries and likewise the bottom grids of the front and rear gages inseries. The strain gage electronics then makes one measurement of thetotal effective strain. One advantage of this method is that only onemeasurement must be made, however the effective strain measured on eachcomposite grid will be lower, which may reduce the precision andaccuracy of the measurement.

TABLE 1 Design similar to FIG. 5, 1000 N load, 50 mm from crank arm faceSG-FT SG-FB SG-BT SG-BB Back Front Total Strain −512 512 303 −304 −6071024 417 (ppm or με) Top Bot Total −209  209 417

Measuring the front and back gages independently may be preferablebecause making separate measurements can be easily executed with theelectronics and will likely yield more accuracy and precision in theoutput.

In order to directly measure the total input torque, both the left andright crank arms may be instrumented as described above. The straingages on each arm may be connected to a common set of measurementelectronics via wires routed through the bottom bracket axle.Alternatively, each arm may have its own complete set of measurementelectronics and may transmit the data to, for example, a handlebarmounted cycle computer that would sum the torque of the two arms. Such acycle computer might be remotely mounted with a separate display mountedin the cyclist's view, or may be a fully integrated display and computerunit with the display mounted in the cyclist's field of view. The cyclecomputer would then be able to display the left vs. right power balance,and may also provide logging of the data for later review.

An alternative embodiment of a power measuring system according to thepresent disclosure might be to instrument only a single crank arm andmeasure the input torque from one leg only. This embodiment would notmeasure the total input torque from the rider but would extrapolate atotal torque. Most riders apply output roughly equal torque with eachleg, so under most conditions simply doubling the measured torque maygive a good estimate of total torque. While the spider approachdescribed above included electronics on only one side of the bike, thetotal torque input by the rider and transmitted to the chain wasmeasured.

Although this single crank arm measurement embodiment might be lessaccurate than the spider based system described above, it may haveseveral advantages. Namely, using a single instrumented crank armrequires replacing fewer parts of the bicycle and has only one set ofelectronics at the crankset.

In both the spider and crank arm based approaches, there are a number ofelectrical functions that may be executed. These functions and thedesign requirements for components to accomplish these functions may besimilar between the two approaches.

There are a number of electronic functions that may be executed at thecrankset. The strain gages may be connected to electronics to measurethe resistance of the strain gages. The strain gage measurementcomponents may then be connected to a microcontroller that controls allfunctions and manipulates the data. The microcontroller may then passthe data to RF transmission components. The RF components transmit thedata to a computer mounted elsewhere on the bicycle, for example but notlimited to the handlebar. Additional components may include hall-effectsensors or accelerometers for cadence measurement.

Alternatively, the microcontroller may be wired to the other componentsof the power measurement system. While wires may be vulnerable todamage, removing electrical components such as the RF components mayreduce battery drain and improve reliability of the power measuringsystem.

Circuitry is also required to power the electronics embedded on thespider or crank arm. This will likely be achieved with a small battery.The power consumption of the embedded electronics may be aggressivelyminimized in order to minimize battery size and weight and maximizebattery life. Power reduction strategies may include changing the datatransmission rate depending on the power level, i.e. at zero power nodata is transmitted, at low power levels the data may be averaged over aseveral seconds, and at high power levels more data is transmitted.

Cadence is a component of the power calculation and can be measured witha variety a methods. One method is to use a hall-effect sensor(s) in thespider or crank arm and a magnet(s) affixed to the frame of the bike,such that the hall-effect sensor is tripped on each revolution. Multiplehall-effect sensors or magnets may be used to receive multiple pulsesper revolution.

Alternatively, an accelerometer can be used to measure the direction ofgravity relative to the orientation of the crank. This can be achievedthrough the use of a single or dual axis accelerometer. A single axisaccelerometer will give the magnitude of the gravitational pull,alternating from +1 g to −1 g. A dual axis accelerometer measuresacceleration in two directions perpendicular to each other, eachalternating from +1 g to −1 g. Some basic calculations will yield theangle and angular velocity of the crank.

Two other methods of determining cadence look closely at the torqueprofile measured from the spider.

One method is to analyze a time based total spider torque profile. Dueto the natural biomechanics of the pedaling action, there will be twodistinct torque pulses as each leg passes through the 3 o'clock positionand has maximum leverage. By identifying these torque peaks andmeasuring their frequency, pedaling cadence can be determined.

As this method of determining cadence is based on cyclist biomechanics,a similar approach may be applied to the torque profile determined by acrank arm approach. The crank arm should show the greatest torqueapplied by the cyclist at the 3 o'clock position and this peak should bedistinct from the amplitude of the torque applied at any other position.Based on this, the spacing of the peak torque recorded by a crank armgage may be used to derive cadence.

The other method involves looking at the torque on each spider armindividually. The spider arms closest to the chain contact point at the12 o'clock position will show the greatest torque. By looking for thisstrain maximum on each spider arm individually it is possible todetermine when each spider arm passes the chain contact point. Thefrequency will yield the pedaling cadence. Note that this method is notdependent on the Rider's biomechanics.

The embodiments of the inventions disclosed herein have been discussedfor the purpose of familiarizing the reader with novel aspects of thepresent invention. Although preferred embodiments have been shown anddescribed, many changes, modifications, and substitutions may be made byone having skill in the art without unnecessarily departing from thespirit and scope of the present invention. Having described preferredaspects and embodiments of the present invention, modifications andequivalents of the disclosed concepts may readily occur to one skilledin the art. However, it is intended that such modifications andequivalents be included within the scope of the claims which areappended hereto.

1. An input torque measuring device for a drive train of a bicycle, thedrive train including a first crank arm and a second crank armconfigured to be engaged by a rider of the bicycle at an outboard end,an inboard end of each crank arm rotatably mounted to the bicycle at abottom bracket of the bicycle, at least one generally planar chain ringoriented generally perpendicular to the bottom bracket and configured torotate about the bottom bracket and to rotate a driven wheel of thebicycle, the device comprising: a spider connected to a first crank armadjacent the bottom bracket and extending out to and directly supportingthe at least one chain ring, the spider configured to transmit forceapplied to the crank arms directly to the at least one chain ring; thespider including a plurality of sensors configured to respond to theforce applied by the spider to the at least one chain ring and producean electronic signal relative to the force transmitted by the spider tothe at least one chain ring, each sensor oriented to be generallyparallel to a plane of the at least one chain ring; an electroniccircuit configured to receive the electronic signals from each sensor ofthe spider.
 2. The input torque measuring device of claim 1, furthercomprising the spider including a plurality of arms extending from acenter of the spider out to the at least one chain ring, each spider armincluding a sensor.
 3. The input torque measuring device of claim 2,wherein each spider arm includes an opposed pair of sensors.
 4. Theinput torque measuring device of claim 1, wherein each sensor is aresponds to a deflection of a portion of the spider when the force istransmitted from the spider to the at least one chain ring.
 5. An inputtorque measuring device for a drive train of a bicycle, the drive trainincluding a first crank arm and a second crank arm configured to beengaged by a rider of the bicycle at an outboard end, an inboard end ofeach crank arm rotatably mounted to the bicycle at a bottom bracket ofthe bicycle, at least one generally planar chain ring oriented generallyperpendicular to the bottom bracket and configured to rotate about thebottom bracket and to rotate a driven wheel of the bicycle, the devicecomprising: a spider connected to a first crank arm adjacent the bottombracket, the spider including a plurality of spider arms extending outto and directly supporting the at least one chain ring, the spiderconfigured to transmit force applied to the crank arms through thespider arms to the at least one chain ring; the spider including aplurality of sensors configured to respond to the force applied by thespider to the at least one chain ring and produce an electronic signalrelative to the force transmitted by the spider to the at least onechain ring; each sensor mounted to a spider arm and comprising a straingrid oriented parallel to a plane of the at least one chain ring; anelectronic circuit configured to receive the electronic signals fromeach sensor of the spider.
 6. The input torque measuring device of claim5, further comprising each spider arm including at least one sensor. 7.The input torque measuring device of claim 5, each sensor furthercomprising a pair of strain grids, the strain grids of each pairoriented perpendicular to each other.
 8. The input torque measuringdevice of claim 5, each sensor mounted to a shear web defined in thespider arm.
 9. The input torque measuring device of claim 8, furthercomprising each shear web having a pair of perpendicularly arrangedstrain grids mounted on opposite sides of the shear web.
 10. The inputtorque measuring device of claim 9, the shear web further including anopening permitting electrical connection of the sensors on oppositesides of the shear web.
 11. The input torque measuring device of claim5, wherein each spider arm is symmetrical about at least one axis. 12.The input torque measuring device of claim 8, further comprising theshear web defined in a recess on the spider arm, the sensor mountedwithin the recess, and a protective covering provided over the sensorwithin the recess.
 13. The input torque measuring device of claim 12,wherein the protective covering is formed from an material at leastpartially filling the recess and laying directly on the sensor.
 14. Aninput torque measuring device for a drive train of a bicycle, the drivetrain including a first crank arm and a second crank arm configured tobe engaged by a rider of the bicycle at an outboard end, an inboard endof each crank arm rotatably mounted to the bicycle at a bottom bracketof the bicycle, at least one chain ring mechanically connected to thecrank arms and configured to rotate a driven wheel of the bicycle, thedevice comprising: at least one of the crank arms including at least onestrain measurement device configured to generate an electronic signalwhen a force is applied to the crank arm, the electronic signal relativeto the force applied to the crank arm; circuitry configured to receivethe electronic signal from the strain gage.
 15. The input toquemeasuring device of claim 14, further comprising the at least one strainmeasurement device includes at least one strain gage oriented generallyperpendicular to a rotational axis of the crank arm.
 16. The inputtorque measurement device of claim 15, further comprising the at leastone strain gage including a pair of strain grids oriented generallyperpendicular to each other.
 17. The input torque measurement device ofclaim 15, further comprising a shear web defined in the crank arm withthe at least one strain gage mounted on opposite sides of the shear web.18. The input torque measuring device of claim 14, further comprising apair of strain measurement devices mounted on opposite each other onopposite sides of the crank arm and generally parallel to each other.19. The input torque measuring device of claim 18, further comprisingboth strain measurement devices oriented generally perpendicular to therotational axis of the crank arm
 20. The input torque measuring deviceof claim 18, wherein the crank arm is generally symmetrical about atleast one axis adjacent the location of the strain measurement devices.21. The input torque measuring device of claim 18, further comprising ashear web defined in the crank arm and the strain measurement devicesare mounted on opposite sides of the shear web.
 22. The input torquemeasuring device of claim 18, wherein the crank arm is a hollow memberdefining an internal recess and the strain measurement devices arepositioned within the recess on opposite sides.